Air conditioning apparatus equipped with a compressor and a vortex

ABSTRACT

An air-conditioner comprises, in an accommodating structure: an axial compressor powered by a built-in motor unit which circulates air, an axial flow-straightening stator to create a static pressure in excess of atmospheric pressure by transferring the air stream obtained in a static centrifugal compressor that creates a rotational flow with the air stream being routed through an axial flow-straightener/diffuser. The flow-straightener/diffuser is internally hollow to circulate ambient air and, externally, straightens the turbulent flow into an axial flow and relieves the pressure. A transfer valve is adapted to the flow-straightener/diffuser to selectively regulate the flow of hot air with the addition of ambient air. A vortex accelerates the air stream using a turbulence effect before it enters an expansion chamber that produces cold and directs the air stream into a final air control valve under the selected temperature conditions.

The invention relates to the technical field of reversible air conditioning apparatus which can distribute warm air or cold air.

The current technology used in air-conditioners and their components has several major drawbacks. The first drawback is that they create condensation due to the heat exchanges that are inherent in the compression of certain gases. The second drawback is the fact that current air-conditioners are often associated with refrigerants which produce gases that are harmful to the environment and have a much greater greenhouse-warming potential than that of CO₂ (up to 2000 times greater), refrigerant leaks are frequent and end-of-life recycling is restricted. Although they use filtration devices, it seems that current air conditioning systems sometimes act as a source which allows the growth and propagation of certain bacteria which cause legionnaires' disease. Extensive research has been conducted by a very large number of air-conditioning manufacturers but, in practice, it is apparent that all or some of the above-mentioned drawbacks remain.

The Applicant's approach was therefore to work towards a design that is radically different to the designs of current air-conditioners in order to overcome, in particular, the problems associated with condensation and the removal of condensates.

Thus, the first sought-after object of the invention was to eliminate condensation effects by no longer using those air-conditioner components which produce condensation and therefore no longer use refrigerants.

The second sought-after object of the invention was to devise a new air-conditioner making it possible to prevent any phenomenon that constitutes an environmental pollution hazard.

The third sought-after object was to devise an air conditioner that can be manufactured under highly competitive economic conditions compared with current air-conditioners and which has an extremely wide variety of applications.

Another sought-after object was to devise an air-conditioner having a new layout which allows very easy adaptation of the heating and cooling effect it produces and which can be controlled by computerised means.

These objects and others will become apparent from the following description.

The concept used by the air-conditioner uses fluid mechanics without the addition of a gas in order to fulfil the desired functions.

According to a first aspect of the invention, the air-conditioner is distinctive in that it comprises, arranged and laid out in an accommodating structure, successively, a first means in the form of an axial compressor equipped with blades around its periphery and powered by a built-in motor unit which circulates air at a given velocity, a second means in the form of an axial flow-straightening stator, the function whereof is to create a static pressure in excess of atmospheric pressure by transferring the air stream obtained in a third means in the form of a static centrifugal compressor whereof the function is to create a rotational flow with a static pressure which varies depending on the temperature rise along the flow, the air stream being routed through a fourth means comprising an axial flow-straightener/diffuser, said flow-straightener being internally hollow in order to circulate ambient air and fulfilling, externally, the function of straightening the turbulent flow into an axial flow and relieving the pressure and in that a fifth means comprising a transfer valve adapts itself around the fourth means in order to regulate or not regulate the flow of hot air with the addition of ambient air and in that a sixth means consisting of a vortex makes it possible to accelerate the stream of air with a turbulence effect before it enters a seventh means consisting of an expansion chamber which produces cold and directing the air stream into the final air control valve under the selected temperature conditions and in that all of said means are arranged in a protective, connecting enclosure.

These aspects and others will become apparent from the following description.

The object of the present invention is described, merely by way of example, in the accompanying drawings in which:

FIG. 1 is a perspective view of an air-conditioning plant in accordance with the invention.

FIG. 2 is a view of all the components of the air-conditioner when it is assembled, the protective structure which houses them is not shown.

FIG. 3 is a view which is essentially similar to that in FIG. 2 but shows an exploded view of part of the built-in motor drive used to operate the axial compressor.

FIG. 4 is a view of the first means comprising the axial compressor viewed from the front.

FIG. 5 is a top view of the axial compressor shown in FIG. 4.

FIG. 6 is a top view of the second means comprising the axial flow-straightening stator.

FIG. 7 is an axonometric view of the third means comprising the static centrifugal compressor.

FIG. 8 is an isometric view of the third means shown in FIG. 7.

FIG. 9 is a partial view of the lane defined by the successive blades along an air stream from the static centrifugal compressor.

FIG. 10 is an axonometric view of the fourth means comprising the axial flow-straightener/diffuser.

FIG. 11 is a perspective view of the fifth means comprising the transfer valve.

FIG. 12 is a perspective view showing assembly of the axial flow-straightener/diffuser on the transfer valve.

FIG. 13 is a view of the sixth means comprising the vortex.

FIG. 14 is a view showing assembly of the axial compressor, axial flow-straightening stator and motor assembly.

FIG. 15 is a view showing assembly of the components in the protective and retaining structure before assembly of the two half-shells of said structure.

FIG. 16 is a perspective view, as in FIG. 13, showing the design of the motor unit which drives the axial compressor.

FIG. 17 is a perspective view, as in FIG. 16, of the motor unit with the axial flow-straightening stator fitted.

In order that the object of the invention may more readily be understood, the following description is given, merely by way of example, reference being made to the accompanying drawings.

The air conditioning apparatus according to the invention is represented in its entirety as (A) and is installed in a plant (I) which is shown in FIG. 1. The air conditioning apparatus is fitted in an external protective housing (1) designed with fixing brackets (1 a) or any other mounting brackets. This housing has a parallelepiped shape, for example, and comprises lateral end flanges (1 b) (1 c) on which there are provided means which are known in themselves, namely, on flange (1 b), a duct (2) which opens into a dual-flow air control valve (3), and an air control valve (4) which opens into a duct (5) associated with an air inlet duct (6) attached to an appropriate support plane (P), wall or the like. This air distribution duct also accommodates a carbon air purification filter device (7) for the air inlet. At the outlet of the air-conditioner, there is, on flange (1 c), a hot or cold air outlet duct (8) which opens into an outlet and discharge duct (9) which is also attached to the appropriate support plane (P).

The characteristics of the air-conditioner and its various component parts are described below.

This air-conditioner comprises a plurality of means laid out and arranged successively in alignment in an accommodating structure (10) which is itself enclosed in and protected by above-mentioned housing (1). Structure (2) has a cylindrical configuration, for example, and is made as two cylindrical half-shells (10 a-10 b) which, along their outer longitudinal edge, have strips (10 c) which make it possible to join and fix them together using bolt type fasteners or other means. The various components of the air-conditioner are thus positioned and attached relative to both each other and the said structure.

The air-conditioner thus comprises:

A first means (11) in the form of an axial compressor fitted with blades (11 a) around its periphery and powered by a built-in motor unit (12) which circulates air at a given velocity;

A second means (13) in the form of an axial flow-straightening stator whereof the function is to create a static pressure in excess of atmospheric pressure by transferring the obtained airstream;

In a third means (14) in the form of a static centrifugal compressor whereof the function is to create a rotational flow with a static pressure that varies depending on the temperature rise along the flow;

A fourth means (15) in the form of an internally hollow axial flow-straightener/diffuser used to circulate ambient air and having, externally, the function of straightening the turbulent flow into an axial flow and relieving the pressure;

A fifth means (16) consisting of a transfer valve which adapts itself around the air flow-straightener/diffuser in order to regulate or not regulate the flow of hot air with the addition of ambient air.

A sixth means (17) consisting of a vortex which makes it possible to accelerate the air stream using a turbulence effect;

A seventh means (18) located at the end of the vortex and constituting an expansion chamber which produces cold in order to direct the air stream into the final air control valve under the chosen temperature conditions.

Each of said means (11 to 18) is now described below more specifically, reference being made to the accompanying drawings.

The various means (11 to 18) are thus represented in the order in which they are assembled in FIGS. 2 and 3; FIG. 3 shows the built-in motor unit associated with the axial compressor.

First means (11) is the axial compressor shown in FIGS. 4 and 5. It comprises a cylindrical body (11 b) which accommodates, around its periphery, a plurality of blades (11 a) made of aluminium, for example, and a front shape (11 c) like a propeller cone. The surface of the blade face of said blades is glass-bead peened, the purpose of this treatment is to harden the corresponding surface in order to compensate for the creep created by rotation of the compressor forming the rotor and prevent deformation of the velocity triangles on the blades. The axial compressor is thus mounted on taper pin (12 a) on the motor unit shown in FIG. 16. Said blades (11 a) have a helical configuration with two adjacent blades having opposite-facing base profiles (11 a 1) which diverge in order to improve the air volume velocity. The velocity triangles of the blades are designed to produce a high-velocity cylindrical axial air flow. The distribution of air streams along the blade remains constant over a single axis so as not to disrupt the air mass in general. The motor unit (12) shown in FIG. 16 thus comprises a shaft (12 b) associated with motor (12 c), protective housing (12 d) and a flange (12 e) for mounting the motor. The end of shaft (12 b) has a conical head (12 a) to receive and support axial compressor (11). Connection of axial compressor (11) to said conical part is obtained in any appropriate manner with the axial compressor being matchingly designed to fit it.

The second means (13) is the axial flow-straightening stator which is attached and joined to enclosure (10) by any appropriate connecting means. The second means (13) is located on the shaft part (12 c) between mounting flange (12 e) and conical part (12 a).

The flow-straightening stator has 10 blades (13 a) made of aluminium, for example. Connection to enclosure (11) is preferably obtained by the tip of blades (13 a). These blades (13 a) are arranged as an extension of blades (11 a) formed on the compressor but, unlike the latter which have a helical configuration, blades (13 a) are arranged in the longitudinal axial direction of the axial flow-straightening stator. They have a symmetrical configuration with a gradual inlet (13 a 1) and a second tapered part (13 a 2) so as to form a teardrop profile. As shown in FIG. 6, examining two successive blades reveals an inlet with convergent profiles and then an outlet with divergent profiles with an intermediate narrowed area with a neck (13 a 3). The forward configuration in the first section of the blades makes it possible to accelerate the airflow and its velocity whereas the second part causes a considerable drop in velocity and helps increase the pressure gradient. The bent geometrical shape of blades (13 a) imparts an appropriate direction to the airflow before admission into the next means, namely the static centrifugal compressor. This axial flow-straightening stator comprises plenum chambers located upstream and downstream from itself; these means are not shown. The purpose of these chambers is to create a static pressure which exceeds atmospheric pressure.

The third means (14) consists of the static centrifugal compressor shown in FIGS. 7, 8 and 9 and is described below.

This compressor (14) comprises a tubular body (14 a) which fits around motor unit (12) and accommodates, according to one particular aspect, two series of primary blades (14 b) and secondary blades (14 c) having different characteristics. The first series of blades (14 b) comprises five blades arranged as a variable-geometry and variable-pitch helix. These primary blades (14 b) are developed so as to make one complete revolution around accommodating body (14 a) in the configuration shown in FIG. 9. Said blades are initially parallel to each other with a preset gap in order to allow positioning of the other series of secondary blades (14 c) which have a much smaller amplitude. Said secondary blades have a twisted configuration which corresponds to the start-up profile of primary blades (14 b), said blades (14 c) being shorter by a ratio of 1 to 2 or 1 to 3. Thus, in the forward part of the static centrifugal compressor, one can observe positioning of all the blades (14 b-14 c) which are arranged alternately with an identical spacing. Given the much shorter length of the secondary blades, the other end of the static centrifugal compressor only reveals the tips of the primary blades. There is therefore tightening of the space between successive blades (14 b) which creates a turbulent flow. The inlet parts of blades (14 b-14 c) are all in the axial longitudinal direction of the body whereas the rear outlet tips of the primary blades are located in a radial plane. It should be noted that, in order to facilitate air circulation, the forward and aft tips of all the different types of blades are tapered.

The surface of each side of the blade is concave and it is not subjected to any particular surface treatment. Thus, static centrifugal compressor (14) makes it possible to transform the axial airflow from means (13) into a rotational flow in order to accelerate it while maintaining the static pressure established at the outlet of axial flow-straightening stator (13).

Centrifugal movement is obtained by reversing the axial airflow along the blades and combining the turbulence effects produced by the various types of blades.

The blades are constructed by projecting several non-ruled surfaces after working out the velocity triangles on the generating line of the centre of mass and the centre of inertia of each surface. These surfaces are then projected by winding onto the final surface of each blade in order to produce a gyrating airflow effect. As soon as a rotational flow is created, this causes an increase in the pressure on the surfaces due to the centrifugal force produced by winding the flow and by restricting the convergent duct between the bearing surfaces. In this phase, the static pressure fluctuates depending on the temperature rise along the entire path.

The characteristics of the fourth means (15) consisting of the axial flow-straightener/diffuser shown in FIG. 10 is described below. The latter is positioned as an axial extension of means (14). It consists of a hollow cylindrical body (15 a) capable of surrounding motor unit (12 c) and allowing ambient air to circulate. On its periphery, the axial flow-straightener/diffuser has a plurality of 14 blades (15 b) made of aluminium, for example, arranged in a curved configuration. The blades in the inlet area have a separation gap which is less than the gap at the rear tip of said blades, thereby creating a divergent effect and the rear tip of the blades is oriented along the longitudinal axis of the flow-straightener. The inlet area for air originating from means (14) is designed to be an extension of the outlet for air originating from means (14). The purpose of this means (15) is to straighten the turbulent airflow into an axial flow and to slightly relieve the pressure in order to reduce the temperature of the circulating air before admission into the sixth means (17) consisting of a vortex. Flow-straightener (15) has a fixed position in enclosure (10) and is fixed in any appropriate manner.

This axial flow-straightener/diffuser is capable of cooperating with and allowing positioning and fitting of a fifth means (16) consisting of a transfer valve. This valve has a cylindrical body (16 a) which fits into the body (15 a) of flow-straightener (15) and it has a projecting skirt (16 b) with a cylindrical configuration. This crown-shaped skirt is designed with a plurality of slits (16 c) which allow air to enter and circulate in body (16 a). On crown (16 b) there is a separately mounted and located ring (20) having a matching shape which is capable of being angularly swivelled relative to said crown (16 b). To achieve this, the ring has solid parts (20 a) in the form of shutters which have shapes and dimensions which match slits (16 c) in order to shut them wholly or partly depending on the position of the ring on crown (16 b). A means of adjusting (21) and driving the ring on the crown is provided on the body of flow-straightener (15) in order to enable appropriate angular orientation of the transfer valve. Depending on the extent to which the transfer valve is opened or closed, it is possible to inject and mix ambient air with air produced and heated by the various means described above.

The sixth means (17) consisting of a vortex is described below. This corresponds to cylindrical disk (17 a) with a central hollow part which accommodates a plurality of 10, for example, blades (17 b) made of aluminium, for example. These blades are arranged in a star shape with a truncated cone configuration. The function of this vortex is to impart a stable, constant velocity to the airflow through rotational movement between the blades and it prepares for transfer of the airflow produced in expansion chamber (18) which produces cold and is located downstream. The latter has a cylindrical configuration with a propeller-cone shaped nose (18 a).

The air conditioning plant made up of all these means makes it possible to produce hot or cold air having temperature ranges adjusted as a function of the applications of the invention using a combination of air circulation effects provided by the various means described.

The motor unit and transfer valve as well as their controls are connected to a digital circuit board which can be controlled by computer via an RS 232 interface or other interface.

The air conditioning plant according to the invention solves the various problems stated earlier. The configuration (11) of the various components and means and the number of blades is given merely by way of example in an attempt to optimise the operation of the air conditioner.

These means can be made of aluminium and, depending on the particular applications of the air conditioners, they can also be made by moulding a plastic, composite or other material, taking into account operating constraints. 

1. Air-conditioner comprising, arranged and laid out in an accommodating enclosure, successively, an axial compressor equipped with blades around its periphery and powered by a built-in motor unit which circulates air at a given velocity, an axial flow-straightening stator to create a static pressure in excess of atmospheric pressure by transferring an air stream obtained in a static centrifugal compressor that creates a rotational flow with a static pressure which varies depending on temperature rise along the flow, the air stream being routed through an axial flow-straightener/diffuser, said flow-straightener/diffuser being internally hollow in order to circulate ambient air and fulfilling, externally, a function of straightening turbulent flow into an axial flow and relieving pressure, and a transfer valve adapted to the flow-straightener/diffuser to selectively regulate flow of hot air with addition of ambient air, a vortex to accelerate the stream of air with a turbulence effect before the air stream enters an expansion chamber which produces cold and directs the air stream into a final air control valve under selected temperature conditions.
 2. Air-conditioner as claimed in claim 1, wherein the axial compressor comprising a cylindrical body which accommodates, around its periphery, a plurality of blades and a front shape like a propeller cone, and the axial compressor is mounted on taper pin of the motor unit, and said blades have a helical configuration with two adjacent blades having opposite-facing base profiles which diverge.
 3. Air-conditioner as claimed in claim 1, wherein the motor unit comprises a shaft associated with a motor, a protective housing, and a flange for mounting the motor, and an end of the shaft has a conical head to receive and support the axial compressor, and the axial compressor is connected to said conical part.
 4. Air-conditioner as claimed in claim 3, wherein the axial flow-straightening stator is attached and joined to the enclosure, and the stator is located on a shaft part between the mounting flange and the conical part, and the stator comprises stator blades arranged as an extension of the blades of the compressor and are arranged in an axial longitudinal direction of the axial flow-straightening stator.
 5. Air-conditioner as claimed in claim 4, wherein the stator blades have a symmetrical configuration with a gradual inlet and a second tapered part so as to form a teardrop profile, and position of two successive stator blades defines an inlet with convergent profiles and then an outlet with divergent profiles with an intermediate narrowed area with a neck.
 6. Air-conditioner as claimed in claim 5, wherein the axial flow-straightening stator includes an upstream and downstream plenum chamber to create a static pressure in excess of atmospheric pressure.
 7. Air-conditioner as claimed in claim 2, wherein the static centrifugal compressor comprises a tubular body which fits around the motor unit and accommodates a series of primary blades and a series of secondary blades having different characteristics.
 8. Air-conditioner as claimed in claim 7, wherein the static centrifugal compressor comprises a first series of primary blades with five blades arranged as a variable-geometry and variable-pitch helix, the primary blades make one complete revolution around the tubular body, and said primary blades are initially parallel to each other with a preset gap in order to allow positioning of the series of secondary blades which have a much smaller amplitude, and said secondary blades have a twisted configuration which corresponds to a start-up profile of the primary blades, said secondary blades being shorter than said primary blades.
 9. Air-conditioner as claimed in claim 8, wherein inlet parts of the primary and secondary blades are all in a longitudinal axial direction of the tubular body, and a rear outlet tips of the primary blades are located in a radial plane, and a surface on each side of each primary blade is concave.
 10. Air-conditioner as claimed in claim 2, wherein the axial flow-straightener/diffuser comprises an axial extension of the static centrifugal compressor and includes a hollow cylindrical body surrounding the motor unit and allowing ambient air to circulate, and, on its periphery, the axial flow-straightener/diffuser has a plurality of peripheral blades in a curved configuration.
 11. Air-conditioner as claimed in claim 10, wherein the periphereal blades in an inlet area have a separation gap which is less than a gap at a rear tip of said peripheral blades, thereby creating a divergent effect, and the rear tip of the peripheral blades is oriented along the longitudinal axis of the flow-straightener/diffuser, and an inlet area for air originating from the static centrifugal compressor is an extension of an outlet for air originating from the static centrifugal compressor
 12. Air-conditioner as claimed in claim 10, wherein the axial straightener/diffuser cooperates with and allows positioning and fitting of the transfer valve, and the transfer valve has a cylindrical body which fits into a body of the flow-straightener/diffuser and has a projecting skirt with a cylindrical configuration with a plurality of slits which allow air to enter and circulate in the cylindrical body, and, on the skirt is a separately mounted and located ring having a matching shape which is capable of being angularly swivelled relative to said skirt, and the ring has shutters which have shapes and dimensions which match slits in order to shut the shutters wholly or partly depending on position of the ring on the skirt, and a means of adjusting and driving the ring on the skirt is provided on the body of the flow-straightener-/diffuser in order to enable appropriate angular orientation of the transfer valve.
 13. Air-conditioner as claimed in claim 2, wherein the vortex comprises a cylindrical disk with a central hollow part which accommodates a plurality of blades, and the blades are arranged in a star shape with a truncated cone configuration, and the vortex imparts a stable, constant velocity to the air flow through rotational movement between the blades and it prepares for transfer of the air flow produced in an expansion chamber located downstream. 